CN107614974A - Boiler, the marine vapor turbine propulsion system with the boiler, the ship and boiler controlling method with the propulsion system - Google Patents
Boiler, the marine vapor turbine propulsion system with the boiler, the ship and boiler controlling method with the propulsion system Download PDFInfo
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- CN107614974A CN107614974A CN201680007926.0A CN201680007926A CN107614974A CN 107614974 A CN107614974 A CN 107614974A CN 201680007926 A CN201680007926 A CN 201680007926A CN 107614974 A CN107614974 A CN 107614974A
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- Prior art keywords
- steam
- temperature
- superheater
- vapor
- hot device
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G5/00—Controlling superheat temperature
- F22G5/16—Controlling superheat temperature by indirectly cooling or heating the superheated steam in auxiliary enclosed heat-exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/02—Arrangement of sensing elements
- F01D17/08—Arrangement of sensing elements responsive to condition of working-fluid, e.g. pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G5/00—Controlling superheat temperature
- F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
- Control Of Turbines (AREA)
Abstract
The present invention has：Steam lead-in path (74a), steam is taken out from the steam taking-up portion (59e) of the half-way of superheater (37)；Steam return path (74b), steam is set to return to the steam return (59f) of superheater (37)；Delay hot device (76), make the temperature of steam reduce；First steam flow adjustment valve (80) and the second steam flow adjustment valve (81), adjust the flow of the steam to slow hot device (76) flowing；And first temperature sensor (72), measure the steam stream downstream of steam return (59f) of superheater (37) and the first vapor (steam) temperature (T1) of the half-way of superheater (37), the present invention, which has, determines superheater outlet temperature (T2) and the superheater outlet temperature relation information (R1) of the relation of the first vapor (steam) temperature (T1), the first steam flow is controlled to adjust valve (80) and the second steam flow adjustment valve (81) so that superheater outlet temperature (T2) turns into desired value according to the measurement result of superheater outlet temperature relation information (R1) and the first temperature sensor (72).
Description
Technical field
The of the invention boiler such as being related to marine boiler, the marine vapor turbine propulsion system with the boiler, with this
The ship and boiler controlling method of marine vapor turbine propulsion system.
Background technology
Boiler is used in order to provide the main steam required by the demand such as steamturbine end.Under normal circumstances, boiler has：
Burner, the burner are burnt in stove；Evaporator, the evaporator be burned device caused by burning gases heating and
Produce steam；And superheater, in the superheater, the steam come from evaporator guiding is overheated so as to produce because of burning gases
Superheated steam.Also, the raising of the thermal efficiency corresponding to demand end, main steaming at higher temperature and higher pressure is required to boiler sometimes
Vapour.For example, in the steamturbine of the propelling screws to driving ship provides the marine boiler of main steam, using with reheating
The reheat boiler peculiar to vessel of device (with reference to patent document 1).In such reheat boiler peculiar to vessel, relative to without reheater with
Toward Marine Boiler, increase main steam temperature and main steam pressure.For example, relative to conventional Marine Boiler, hot pot again peculiar to vessel
The main steam temperature of the superheater outlet of stove brings up to 560 DEG C from 515 DEG C, and main steam pressure brings up to 10MPa from 6MPa.
On the other hand, provided by detecting the outlet temperature of superheater to reduce the vapor (steam) temperature of midway to adjust from boiler
Main steam temperature, pressure.Patent Document 2 discloses following structure following：Although using useless without stove
The structure of thimble-tube boiler, but reduce the vapor (steam) temperature of midway by spraying attemperator.
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2012-167859 publications
Patent document 2：Japanese Unexamined Patent Publication 2006-125760 publications
The invention problem to be solved
When making main steam high temperature caused by boiler as described above, the metal temperature of the heat-transfer pipe of superheater is formed
(metal material temperature) rises, and tackles high temperature and needs to make heat-transfer pipe make metal material advanced using low-alloy steel etc..But
Be, if make heat-transfer pipe metal material it is advanced if can make cost increase.Therefore, in order to not make the metal material of heat-transfer pipe advanced
Change and realize the high temperature of superheated steam, it is desirable to which suitably the metal temperature of the superheater in management operating is to suppress heat-transfer pipe
Metal temperature and obtain desired main steam temperature.
Patent Document 2 discloses obtain superheater outlet main steam temperature and control spraying attemperator flow,
Water supply flow, but following worry be present：When obtaining the main steam temperature of superheater outlet to carry out feedback control, born in boiler
Control delay is produced when load changes and causes the metal temperature of superheater to exceed permissible value.
Also, in patent document 1, increase the heat transfer area of superheater to tackle the high temperature of main steam temperature
Add, superheater is divided into No. 1 superheater and No. 2 superheaters, No. 1 superheater of steam stream upstream side is arranged on stove side, steam
No. 2 superheaters in stream downstream are arranged at the rear of No. 1 superheater relative to stove, thus prevent because of the radiation from stove and
The temperature of caused No. 2 superheaters rises.But even if structure as using, because superheater is by No. 1 superheater and 2 times
Superheater forms and turns into longer steam path, therefore following worry be present：Superheater outlet is being obtained as described above
Control delay can be produced when main steam temperature is to carry out feedback control, temperature, the pressure of main steam become unstable, because of the situation
And the metal temperature of heat-transfer pipe is caused to exceed permissible value.
The content of the invention
The present invention be in view of such situation and complete, its object is to, there is provided following boiler, there is the boiler
Marine vapor turbine propulsion system, the ship and boiler controlling method with the marine vapor turbine propulsion system：It can use up
Possibly avoid the control delay of the main steam temperature of superheater outlet and suitably manage the temperature of superheater.
Means for solving the problems
In order to solve above-mentioned problem, boiler of the invention, the marine vapor turbine propulsion system with the boiler, with should
The ship and boiler controlling method of marine vapor turbine propulsion system use following means.
That is, boiler of the invention is characterised by that the boiler has：Burner, the burner are burnt in stove；
Evaporator, the evaporator produce steam by burning gases caused by the burner；Superheater, the superheater is relative to this
Evaporator is configured at the stove side, and makes steam superheating caused by the evaporator and produce superheated steam；Vapor (steam) temperature
Adjustment unit, returned making the steam from the taking-up of the steam taking-up portion of the half-way of the superheater return to the steam of the superheater
During portion, the vapor (steam) temperature adjustment unit is adjusted to vapor (steam) temperature；Control unit, the control unit control vapor (steam) temperature adjustment single
Member；And first temperature sensor, first temperature sensor is under the steam stream of the steam return of the superheater
First vapor (steam) temperature of trip side and the half-way of the superheater measures, and the control unit has superheater outlet temperature pass
It is information, the superheater outlet temperature relation information determines that the superheater of the vapor (steam) temperature of the outlet as the superheater goes out
The relation of mouth temperature and first vapor (steam) temperature, according to the superheater outlet temperature relation information and first TEMP
The measurement result of device controls the vapor (steam) temperature adjustment unit, so that the superheater outlet temperature turns into desired value.
Superheater outlet temperature after being overheated as superheater is controlled so as to correspond to and wanted as steamturbine using end
The desired value asked.In order to obtain the desired value, the steam temperature that is adjusted using the vapor (steam) temperature of the half-way to superheater
Spend adjustment unit.That is, it have adjusted after the temperature of the steam of the steam taking-up portion of the half-way of superheater taking-up, making this
Steam returns to superheater from steam return, so as to obtain desired superheater outlet temperature.
If in order that superheater outlet temperature only detects superheater outlet temperature to adjust to slow hot device for desired value
If the steam flow of flowing, it is possible to produce control because of the distance between superheater outlet and vapor (steam) temperature adjustment unit and prolong
Late.Therefore, in the present invention, obtain determining the downstream of superheater outlet temperature and steam return and the midway of superheater
The superheater outlet temperature relation information of the relation of first vapor (steam) temperature of position, according to the superheater outlet temperature relation information
Vapor (steam) temperature adjustment unit is controlled with the measurement result of the first temperature sensor, so that superheater outlet temperature is desired value.
Thus, compared with only entering trip temperature adjustment using superheater outlet temperature, control delay can not be produced and go out superheater
Mouth temperature turns into desired value.
As superheater outlet temperature relation information, can be beforehand through experiment and the superheater outlet temperature that determines with
The database of the relation of first vapor (steam) temperature, or can also use according to beforehand through the superheater outlet temperature obtained by experiment
Degree and the relation of the first vapor (steam) temperature and derived function.
Also, control temperature due to obtaining the first vapor (steam) temperature in the half-way of superheater rather than superheater outlet
Degree, the position limitation temperature in the upstream side of superheater outlet, therefore the temperature of superheater can be avoided to become too high situation.
Thereby, it is possible to which the metal temperature of superheater is controlled below setting, situation that can be in superheater without using advanced material
Under ensure the viability of superheater.
In addition, in the boiler of the present invention, it is characterised in that the boiler has to be surveyed to the superheater outlet temperature
The second temperature sensor of amount, the control unit control the vapor (steam) temperature according to the measurement result of the second temperature sensor
Adjustment unit, so that the superheater outlet temperature turns into desired value.
Vapor (steam) temperature adjustment unit is controlled so that mistake according to the superheater outlet temperature measured by second temperature sensor
Hot device outlet temperature turns into desired value, is controlled exactly thus, it is possible to which further superheater outlet temperature is micro-adjusted.
In addition, in the boiler of the present invention, it is characterised in that the superheater has：No. 1 superheater, No. 1 superheater
It is arranged at steam stream upstream side；And No. 2 superheaters, No. 2 superheaters are arranged at the steam stream downstream of No. 1 superheater,
The rear of No. 1 superheater, first steam measured by first temperature sensor are arranged at relative to the stove
Vapor (steam) temperature of the temperature between No. 1 superheater and No. 2 superheaters.
By setting No. 2 superheaters relative to rear side of the stove in No. 1 superheater, so as to compared with No. 1 superheater, make
No. 2 times superheater is not readily susceptible to the radiation from stove.Accordingly, for steam stream than No. 1 superheater downstream and Metal Temperature
No. 2 superheaters that degree (the metal material temperature for forming the heat-transfer pipe of superheater) easily rises by steam, reduce the shadow of radiation
Ring, the metal temperature for thus enabling that No. 2 superheaters is to allow below temperature.Also, in the present invention, due to passing through control unit
To control 1 vapor (steam) temperature between No. 1 superheater and No. 2 superheaters, therefore can suitably manage under 1 vapor (steam) temperature
Swim the temperature of No. 2 superheaters of side.
In addition, in the boiler of the present invention, the vapor (steam) temperature adjustment unit has：Delay hot device, this, which delays hot device, makes guiding
The temperature of the steam come reduces；And delaying hot device flow adjustment unit, the slow hot device is adjusted slow to this with flow adjustment unit
The flow of the steam of hot device flowing.
Use to reduce the vapor (steam) temperature of the half-way of superheater and delay hot device.Also, flowed by slow hot device
Amount adjustment unit make as defined in the steam of amount flow to slow hot device after vapor (steam) temperature is reduced desired amount, make the steam
Superheater is returned to from steam return and obtains desired superheater outlet temperature.
In addition, as hot device is delayed, example is as used in heat-transfer pipe set in the water used in evaporator in bucket
The structure for flowing steam.
In addition, in the boiler of the present invention, it is characterised in that the vapor (steam) temperature adjustment unit has：Steam imports road
Steam is directed to the slow hot device by footpath, the steam lead-in path from the steam taking-up portion；Steam return path, the steam return
Loop footpath makes steam return to the steam return from the slow hot device；And delay hot device bypass path, the slow hot device bypass
Path is connected the steam lead-in path with the steam return path in a manner of getting around the slow hot device, described to delay hot device
Have with flow adjustment unit：First flow adjusts valve, and first flow adjustment valve is arranged at the slow hot device bypass path；With
And second flow adjustment valve, second flow adjustment valve are arranged at the steam return path and the steam return path and institute
State the upstream side of the merging part of slow hot device bypass path.
The steam of steam lead-in path is directed into from superheater to slow hot device to ease up hot device bypass path flowing.To slow heat
The steam of device flowing is being delayed the rear to the flowing of steam return path of hot device desuperheat.On the other hand, to slow hot device bypass runoff
Dynamic steam is not by slow hot device desuperheat and with being collaborated by the steam after slow hot device desuperheat in the merging part of steam return path.
Flow-rate adjustment is carried out by first flow adjustment valve to the steam of slow hot device bypass path flowing.If increase first flow
The aperture of valve is adjusted, then gets around the bypass flow increase of slow hot device, suppresses the steaming after collaborating in the merging part of steam return
The reduction of stripping temperature.On the other hand, if reducing the aperture of first flow adjustment valve, the bypass flow for getting around slow hot device is reduced,
Increasing the temperature of the vapor (steam) temperature after collaborating in the merging part of steam return reduces.
Flow tune is carried out by second flow adjustment valve to the flow that the merging part of steam return flows through too slow hot device
Section.If increasing the aperture of second flow adjustment valve, increased by the flow for delaying hot device, increase the merging part in steam return
The temperature of vapor (steam) temperature behind middle interflow reduces.On the other hand, if reducing the aperture of second flow adjustment valve, by delaying hot device
Flow reduce, suppress in the merging part of steam return collaborate after vapor (steam) temperature temperature reduce.
So, the aperture of valve and second flow adjustment valve is adjusted by adjusting first flow, can control and be returned in steam
Vapor (steam) temperature after collaborating in the merging part in portion.
Also, first flow adjustment valve is not to fix aperture and can carry out aperture adjustment as fixed orifice, because
This can expand temperature adjustment amplitude.Such as cope with the change of amount of heat absorption because of caused by the deterioration year in year out of stove and lead
The increase of the superheat steam temperature of cause.That is, even if second flow adjustment valve is standard-sized sheet, can also be adjusted by increasing first flow
The aperture of valve and carry out the control of vapor (steam) temperature.Thereby, it is possible to by the metal temperature of the superheater in the downstream of steam return
It is securely maintained lower than permissible value.
In addition, in the boiler of the present invention, it is characterised in that the minimum aperture of the first flow adjustment valve is bigger than 0
Defined aperture.
If making the aperture of first flow adjustment valve turn into fully closed for 0, steam will not flow to slow hot device bypass path,
All steam that guiding comes from the steam taking-up portion of superheater, which flow into, delays hot device, therefore has the load that following unfavorable condition occurs
Sorrow：Vapor (steam) temperature excessively reduces and produces substantial amounts of condensed water in hot device is delayed, and produces condensed water and flows into second flow adjustment valve.
Also, if substantial amounts of steam flows into and delays hot device, there is following worry：The larger pressure loss is produced in hot device is delayed, steam takes
The steam pressure for the superheater for going out the upstream side in portion excessively rises.Also, there is following worry：The steaming of the upstream side in steam taking-up portion
The steam pressure of steam-boiler cylinder excessively rises, and sprays steam from the safety valve for being arranged at steamdrum.
Therefore, in the present invention, it is the defined aperture bigger than 0 by the minimum aperture for making first flow adjustment valve, from
And prevent from flowing into from all steam that the guiding of the steam taking-up portion of superheater comes and delay hot device.Thus, prevent delay hot device in because
The generation of condensed water caused by the temperature of steam reduces, and the rising for delaying the pressure loss in hot device is avoided, so as to
Stable operating.
In addition, the minimum aperture of first flow adjustment valve can be fixed value, but it is also contemplated that to the bad year in year out of boiler
Change and can be changed according to operational situations such as the accumulation durations of runs.
Also, the marine vapor turbine propulsion system of the present invention is characterised by, marine vapor turbine propulsion system tool
Have：Steamturbine, steamturbine driving produce the propeller of thrust in water；And the boiler described in above-mentioned any one,
The boiler supplies steam to the steamturbine.
As the driving steam of the steamturbine of the driving propeller such as propeller, using above-mentioned arbitrary boiler, because
This can obtain desired superheater outlet temperature, the navigation that can be stablized.
Also, the ship of the present invention is characterised by thering is above-mentioned marine vapor turbine propulsion system.
Due to above-mentioned marine vapor turbine propulsion system, therefore the ship for the navigation that can be stablized can be provided
Oceangoing ship.
Also, the boiler controlling method of the present invention is characterised by having：Burning gases produce process, produce combustion gas
Body；Steam produces process, and steam is produced by caused burning gases；Superheated steam produces process, makes caused steaming
Vapour overheats and produces superheated steam in the superheater；Superheated steam delays thermal technology's sequence, takes out and steams from the half-way of the superheater
Vapour, and steam is returned to the superheater after it have passed through the slow hot device that the temperature for making the steam reduces；Slow hot device is used
Flow adjusts process, is adjusted by delaying hot device with flow adjustment unit to the flow for delaying the steam that hot device flows；First
Vapor (steam) temperature measures process, to have passed through the superheated steam delay after thermal technology sequence and the half-way of the superheater first
Vapor (steam) temperature measures；And superheater outlet temperature adjustment process, according to superheater outlet temperature relation information and described
First vapor (steam) temperature measurement process measurement result come control it is described delay hot device flow adjustment unit so that the superheater goes out
Mouth temperature turns into desired value, wherein, the superheater outlet temperature relation information determines the outlet as the superheater
The superheater outlet temperature of vapor (steam) temperature and the relation of first vapor (steam) temperature.
Invention effect
In accordance with the invention it is possible to avoid the control of the main steam temperature of superheater outlet from postponing and suitably manage overheat
The temperature of device.
Brief description of the drawings
Fig. 1 is the summary construction diagram for the marine vapor turbine propulsion system for being denoted as an embodiment of the invention.
Fig. 2 is the stereogram for the partial enlargement for representing No. 1 superheater shown in Fig. 1.
Fig. 3 is the summary construction diagram for representing the major part around Fig. 1 superheater.
Fig. 4 is the control block diagram for representing the Main Steam Temperature Control by control unit progress.
Fig. 5 is the figure of the metal temperature for the heat-transfer pipe for representing superheater.
Symbol description
1 steamturbine propulsion system
3 propellers
5 steamturbines
7 boilers
9 high-pressure turbines
11 middle pressure turbines
13 low-pressure turbines
15 retrogressing turbines
17 first rotary shafts
21 second rotary shafts
23 reductors
25 propeller shafts
27 main stoves
29 reheaters
31 stoves
33 main burners (burner)
Bank tube before 35
37 superheaters
38 evaporators
39 evaporation tube groups
41 buckets
43 steamdrums
44 steam feed paths
46 flowmeters
47 main burner fuel distribution tubes
49 main burner fuel flow control valves
51 reheat combustion chambers
53 reheating fuel distribution tubes
55 reheating adjust valve with fuel flow rate
No. 59 1 superheaters
No. 61 2 superheaters
63 superheater outlet pipe arrangements
64 branch points
65 first main steam pipe arrangements
70 main steam temperature sensors (second temperature sensor)
71 middle connecting pipings
72 intermediate steam temperature sensors (the first temperature sensor)
74 vapor (steam) temperatures adjustment line (vapor (steam) temperature adjustment unit)
74a steam lead-in paths
74b steam return paths
76 delay hot device (vapor (steam) temperature adjustment unit)
78 bypass paths (delay hot device bypass path)
80 first steam flows adjustment valve (delaying hot device flow adjustment unit)
81 second steam flows adjustment valve (delaying hot device flow adjustment unit)
85 first comparing and computing unit
86 second comparing and computing unit
87 first adders
88 second adders
Embodiment
Hereinafter, embodiments of the present invention are illustrated referring to the drawings.
The marine vapor turbine propulsion system 1 applied to ship is represented in Fig. 1.Marine vapor turbine propulsion system 1 has：
The propelling screws (propeller) 3 of thrust are produced in water；Apply the steamturbine 5 of revolving force to propeller 3；And to steam
Turbine 5 supplies the boiler 7 of the superheated steam as main steam.
There is steamturbine 5 high-pressure turbine 9, middle pressure turbine 11, low-pressure turbine 13 and retrogressing to use turbine 15.High-pressure turbine
9 and middle pressure turbine 11 link via the first shared rotary shaft 17.Low-pressure turbine 13 and retrogressing are with turbine 15 via shared
Second rotary shaft 21 and link.First rotary shaft 17 is arranged side-by-side with the second rotary shaft 21, and respective output end is connected to deceleration
Machine 23.Propeller 3 is connected via propeller shaft 25 with reductor 23.
Boiler 7 uses reheat boiler peculiar to vessel, and the reheat boiler peculiar to vessel is compactly designed to be able to be arranged in ship, and
With reheater 57.
Boiler 7 has main stove 27 and reheater 29.It is provided with main stove 27：Hollow stove 31, it is arranged at stove 31
The main burner (burner) 33 on top, the preceding bank tube 35 for circulation of internally supplying water, superheater 37 and evaporator 38.
The wall portion of stove 31 is made up of the water screen tube (not shown) for circulation of supplying water.Pass through main combustion from fuels sources (not shown)
Burner supplies fuel with fuel distribution tube 47 to main burner 33.Main burner fuel distribution tube 47 is provided with the confession of regulation fuel
Main burner fuel flow control valve 49 to amount.
Evaporator 38 has：It is set as the evaporation tube group 39 of more vertically extending heat-transfer pipes；Bucket 41, the water
Bucket 41 is connected with the lower section of evaporation tube group 39, and internally stores water；And steamdrum 43, the steamdrum 43 and evaporation tube
The top connection of group 39.
Reheater 29 is configured at the rear trip side of the evaporation tube group 39 of main stove 27 vertically extendingly, and is configured to turn into
The path of burning gases as caused by the burning of main burner 33.The bottom of reheater 29 is provided with reheat combustion chamber 51.
From fuels sources (not shown) by reheating fuel is supplied with fuel distribution tube 53 to reheat combustion chamber 51.In reheating fuel distribution tube 53
It is provided with the reheating fuel flow control valve 55 of the quantity delivered of regulation fuel.The top of reheater 29 is provided with reheater
57, the reheater 57 has internally for the heat-transfer pipe of steam circulation.
Superheater 37 has No. 1 superheater 59 and No. 2 superheaters 61, turns into relative to combustion gas flow using 2 row
Structure.No. 1 superheater 59 and No. 2 superheaters 61 bend to down U-shaped with multiple in a manner of U-shaped turning part is above respectively
Heat-transfer pipe 59a, 61a of shape.No. 1 superheater 59 is configured in the downstream of stove 31 relative to preceding bank tube 35, also, relatively
The upstream side of stove 31 is configured in No. 2 superheaters 61.On steam stream, No. 1 superheater 59 and No. 2 tandems of superheater 61
Connection, No. 1 superheater 59 is upstream side, and No. 2 superheaters 61 are downstream.
The the first joint 59b and the second joint being connected with heat-transfer pipe 59a lower end are provided with the lower section of No. 1 superheater 59
59c。
As shown in Fig. 2 the first joint 59b and the second joint 59c be provided with a prescribed interval by inside points every it is more
Multiple rooms are divided into individual demarcation strip 59d, each joint 59b, 59c.Heat-transfer pipe 59a is by the room and second in the first joint 59b
Room in joint 59c connects into alternately circulates for steam.Thus, the steam in the first joint 59b is directed into via heat transfer
Pipe 59a flows to the second joint 59c, is then alternately flowed successively in each room in each joint 59b, 59c.
In this manual, the path for the heat-transfer pipe for flowing to another joint from a joint for steam is referred to as passage
(pass).According to this definition, figure 2 illustrates two passages.Also, as shown in figure 3, No. 1 superheater 59 be provided with from
First passage I to the 6th passage VI six passages.
As shown in figure 1, the first joint 61b being connected with heat-transfer pipe 61a lower end is provided with the lower section of No. 2 superheaters 61
With the second joint 61c.The structure of No. 2 superheaters 61 is identical with No. 1 superheater 59 shown in Fig. 2, is set in each joint 61b, 61c
Demarcation strip 61d (reference picture 3) is equipped with, is connected with heat-transfer pipe 61a to cause room of the steam in the first joint 61b and the second joint
Alternately circulated in room in 61c.As shown in figure 3, it is provided with No. 2 superheaters 61 from the 7th passage VII to the tenth passage X's
Four passages.
In addition, in the present embodiment, No. 1 superheater 59 uses six passages, and No. 2 times superheater 61 uses four passages,
But the invention is not restricted to this or other numbers of channels.
As shown in figure 3, the steam of No. 1 superheater 59 is directed into 1 from steamdrum 43 via steam feed path 44
Flowed in secondary superheater 59 by six passages.Steam afterwards is directed into No. 2 superheaters 61, in No. 2 superheaters 61
Four passages are have passed through, are then directed into high-pressure turbine 9 (or retrogressing turbine 15) via superheater outlet pipe arrangement 63.
As shown in figure 1, superheater outlet pipe arrangement 63 is branched at branch point 64 is directed to high-pressure turbine 9 by main steam
The first main steam pipe arrangement 65 and main steam is directed to the second main steam pipe arrangement 67 of retrogressing turbine 15.In the first main steaming
Automobile fitting pipe 65 is provided with the first open and close valve 66, and the second main steam pipe arrangement 67 is provided with the second open and close valve 68.By (not shown)
Control unit is optionally opened and closed to the first open and close valve 66 and the second open and close valve 68, is thus used to high-pressure turbine 9 or retrogressing
Any one party supply main steam in turbine 15.In addition, though it is not shown, but between the first open and close valve 66 and high-pressure turbine 9
And second open and close valve 68 and retrogressing with the steam that adjustment steam flow is provided between turbine 15 add and subtract valve, by control unit come
Adjust the output of steamturbine 5.
In the case where have selected the first open and close valve 66, after main steam is supplied to high-pressure turbine 9, high-pressure turbine 9
Outlet vapor is imported into the upstream end thereof of the top of reheater 57, passes through burning gases caused by the burning of main burner 33
The burning gases of after-heat and reheat combustion chamber 51 and be reheated.Reheated steam after being reheated by reheater 57 is from reheating
The downstream end of the lower section of device 57 is directed to middle pressure turbine 11.The outlet vapor of middle pressure turbine 11 is supplied to low-pressure turbine
13, after rotation driving has been carried out to low-pressure turbine 13, it is sent to condenser 69.Water after being liquefied by condenser 69 is supplied to
To boiler 7.
On the other hand, in the case where have selected the second open and close valve 68, main steam is supplied to retrogressing turbine 15, to rear
Move back the steam after having carried out rotation driving with turbine 15 and be sent to condenser 69.
Revolving force is passed to via reductor 23 by propeller shaft 25 by the work of such steamturbine 5, makes spiral shell
Rotation oar 3 rotates.
Then, the steam stream centered on superheater 37 is illustrated using Fig. 3.Superheater 37 is illustrated in the figure
The major part structure of surrounding.Six passages having from first passage I to the 6th passage VI are formed in No. 1 superheater 59.2
Four passages having from the 7th passage VII to the tenth passage X are formed in secondary superheater 61.
Steam in the steamdrum 43 of evaporator 38 (reference picture 1) is directed into 1 mistake via steam feed path 44
First joint 59b of hot device 59 entrance.Steam feed path 44 is provided with detection steam flow F flowmeter 46.As
Flowmeter 46, such as use differential pressure flowmeter.The load of boiler 7 is grasped according to the steam flow F obtained by flowmeter 46.
Pass through the main steam temperature sensor (second temperature of the first joint 61b for being arranged at No. 2 superheaters 61 export department
Sensor) 70 detect the main steam temperature T2 as the superheat steam temperature of No. 2 superheaters 61.Main steam temperature sensor 70
Output be sent to control unit (not shown).Connect in addition, the set location of main steam temperature sensor 70 can not be first
Head 61b export department, as long as can detect by No. 2 superheaters 61 and overheat after superheat steam temperature position, also may be used
To be other positions, such as it is arranged at superheater outlet pipe arrangement 63.
The middle connecting pipings 71 for connecting No. 1 superheater 59 and No. 2 superheaters 61 is provided with intermediate steam temperature to pass
Sensor (the first temperature sensor) 72.The steam flowed in superheater 37 is measured by intermediate steam temperature sensor 72
The intermediate steam temperature T1 of half-way.The output of intermediate steam temperature sensor 72 is sent to control unit (not shown).
In present embodiment, intermediate steam temperature T1 is the outlet temperature of No. 1 superheater 59, i.e., the inlet temperature of No. 2 times superheaters 61.
The first joint 59b after it have passed through the fourth lane IV of No. 1 superheater 59 is provided with steam taking-up portion 59e,
It is connected with the steam lead-in path 74a of vapor (steam) temperature adjustment line (vapor (steam) temperature adjustment unit) 74 upstream end.Also, at 1 time
First joint 59b of the Five-channel V of superheater 59 upstream side is provided with steam return 59f, and line is adjusted with vapor (steam) temperature
74 steam return path 74b downstream connection.Guided from steam taking-up portion 59e by the steam of whole from No. 1 superheater 59
Line 74 is adjusted to vapor (steam) temperature, the whole steam for being directed into vapor (steam) temperature adjustment line 74 return to 1 from steam return 59f
Secondary superheater 59.
In vapor (steam) temperature adjusts line 74, in steam lead-in path 74a downstream and the upstream side of steam return path
It is provided with the slow hot device 76 for reducing vapor (steam) temperature.Delaying hot device 76 has the heat-transfer pipe being configured in the water in bucket 41.Pass through
Water in bucket 41 is cooled in the steam of the heat transfer Bottomhole pressure from the outside of heat-transfer pipe.
Bypass path (the slow hot device bypass for getting around slow hot device 76 for steam and flowing is provided with vapor (steam) temperature adjustment line 74
Path) 78.The first steam flow that adjustment steam flow is provided with bypass path 78 adjusts valve 80.First steam flow adjusts
The valve opening of valve 80 is controlled by control unit (not shown).
In the steam return path 74b in downstream of hot device 76 is delayed, more top than with the merging part 78a of bypass path 78
The position of trip side is provided with the second steam flow adjustment valve 81 of adjustment steam flow.The valve of second steam flow adjustment valve 81 is opened
Degree is controlled by control unit (not shown).
The first steam flow is controlled to adjust the aperture that the steam flow of valve 80 and second adjusts valve 81 by control unit, thus
The ratio of steam flow flowed to slow hot device 76 is determined, controls the amount of cooling water of the steam come from No. 1 guiding of superheater 59.Specifically
For, the ratio of the steam flow flowed to slow hot device 76 is bigger, then the amount of cooling water of steam is bigger.
So, in the present embodiment, the steam between the fourth lane IV and Five-channel V of No. 1 superheater 59 is taken out
And adjust vapor (steam) temperature.
Control unit passes according to the main steam temperature T2 obtained by above-mentioned main steam temperature sensor 70, intermediate steam temperature
Steam flow F obtained by intermediate steam temperature T1, flowmeter 46 obtained by sensor 72 etc. and control into desired main steam
Temperature.Control unit is for example by CPU (Central Processing Unit：CPU), RAM (Random Access
Memory：Random access memory), ROM (Read Only Memory：Read-only storage) and depositing of can reading of computer
Storage media etc. is formed.Also, as one, for realizing that a series of processing of various functions is stored in the form of program
Storage medium etc., CPU read the program in RAM etc., processing/calculation process of execution information, are achieved in various functions.Separately
Outside, program can also be applied and is installed on ROM, the form of other storage mediums in advance, can be read with being stored in computer
Storage medium in state be provided form, via wired or wireless means of communication come form for distributing etc..Calculate
The storage medium that machine can be read refers to disk, CD, CD-ROM, DVD-ROM, semiconductor memory etc..
Then, the Main Steam Temperature Control of control unit is illustrated using Fig. 4.
Control unit has in defined memory：The first control on main steam temperature T2 and intermediate steam temperature T1
Function (superheater outlet temperature relation information) R1；It is relevant with the go-ahead signal for being applied to two steam flow adjustment valves 80,81
The second control function R2；Relevant the 3rd control function R3 of opening degree instruction with being applied to the first steam flow adjustment valve 80；
And the fourth control function R4 relevant with being applied to the opening degree instruction of the second steam flow adjustment valve 81.
Alternatively, it is also possible to substitute these control functions R1~R4, and the control with digitized database is used to compare
Figure.
First control function R1 represents the relation of intermediate steam temperature T1 corresponding with main steam temperature T2 anticipation temperature.
That is, in the case where boiler 7 is defined loads, obtained previously according to the result tested, simulated in order to obtain desired master
The anticipation temperature of intermediate steam temperature T1 needed for vapor (steam) temperature T2.For example, in the case where boiler 7 is nominal load, obtain
Following relation：In order that target main steam temperature is 560 DEG C, it is necessary to which the anticipation temperature for making intermediate steam temperature T1 is 480 DEG C.This
Outside, the first control function R1 changes intermediate steam temperature T1 anticipation temperature according to the load of boiler 7.Specifically, as being somebody's turn to do
Shown in figure, in the case where boiler load is lower than defined value, the steam flow F (STM FLOW (T/ i.e. obtained by flowmeter 46
H in the case that)) value is low than as defined in, make intermediate steam temperature T1 anticipation temperature constant, it is big to compare defined value in boiler load
In the case of, value as defined in the steam flow F ratios i.e. obtained by flowmeter 46 it is big in the case of, using according to steam flow F's
The relation for increasing and making intermediate steam temperature T1 anticipation temperature diminish.So in being reduced in the case that steam flow F is larger
Between vapor (steam) temperature T1 anticipation temperature the reasons why it is as follows：Steam flow F is larger to mean that boiler load is larger, it is contemplated that 1 mistake
The temperature of hot device 59 and No. 2 superheaters 61 is in rising trend, therefore reduces intermediate steam temperature T1 and maintain appropriate metal
Temperature.
The opening degree instruction that second control function R2 adjusts valve 80,81 to two steam flows applies go-ahead signal.For example, as being somebody's turn to do
Shown in figure, apply larger go-ahead signal when steam flow F increases, and add the work of two steam flows adjustment valve 80,81
Speed is so as to improving the tracing ability of vapor (steam) temperature.Also, it is radically increased leading letter after steam flow F has exceeded defined value
Number, and accelerate the initial startup of control so as to suppressing the variation of vapor (steam) temperature.
3rd control function R3 is the function for the opening degree instruction for applying the first steam flow adjustment valve 80.First steam flow
The adjustment decision of valve 80 gets around the steam flow of slow hot device 76, and aperture more increases, and more substantial amounts of steam gets around the slow (reference of hot device 76
Fig. 3), it is suppressed that the temperature of steam reduces.In contrast, when the first steam flow adjustment valve 80 aperture reduce when, guide to
The steam for delaying hot device 76 becomes more, and the temperature of steam, which reduces, becomes big.Therefore, as shown in the drawing, the 3rd control function R3 turns into as follows
Function：The control output valve being applied in is bigger (i.e. bigger in high temperature side with the temperature difference of target temperature), then opening degree command value is got over
Decline to the right as small.Also, in the 3rd control function R3, even if control output valve becomes big, also do not make opening degree command value
For 0%, but maintain 10% defined aperture.Furthermore, it is contemplated that such as the deterioration year in year out of boiler 7, can be as needed
Change the 10% minimum aperture.Also, refer to entirely on the opening degree command value of the first steam flow adjustment valve 80,100%
Open, 0% refer to it is fully closed.
4th control function R4 is the function for the opening degree instruction for applying the second steam flow adjustment valve 81.Second steam flow
Adjustment valve 81 determines the steam flow to slow hot device 76 (reference picture 3) flowing, aperture more increase then more substantial amounts of steam to slow heat
Device 76 flows, and reduces the temperature of steam and becomes big.In contrast, when the aperture of the second steam flow adjustment valve 81 is reduced, draw
The steam for being oriented to slow hot device 76 tails off, it is suppressed that the temperature of steam reduces.Therefore, as shown in the drawing, the 4th control function R4 into
For such as minor function：The control output valve bigger (i.e. bigger in high temperature side with the temperature difference of target temperature) being applied in then opening degree instruction
Rise to the right as value is bigger.Also, in the 4th control function R4, (the i.e. target temperature in the case where controlling output valve to be 0
In the case that degree is consistent with present situation temperature), it is 0% to make opening degree instruction, steam is not flowed to slow hot device 76.On the other hand, when
Control output valve be as defined in the value above when opening degree instruction be 100%.In addition, the aperture on the second steam flow adjustment valve 81
Command value and the first steam flow adjustment valve 80 are identical, and 100% refers to standard-sized sheet, 0% refer to it is fully closed.
First steam flow adjustment valve 80 and second steam flow adjustment valve 81 uses the valve of identical capacity, with each control
The mode for adding up to aperture to be 100% in output valve sets the 3rd control function R3 and the 4th control function R4.Thus, steaming is passed through
It is constant that stripping temperature adjustment line 74 (reference picture 3), which takes out the steam flow again returned to afterwards from No. 1 superheater 59, can be realized
Stable control.But as shown in the 3rd control function R3, in the case where control output valve is larger, opening degree command value will not be into
For 0% scope (opening degree command value scope constant when being in the 10% of minimum aperture) not limited to this.
The intermediate steam temperature T1 from intermediate steam temperature sensor 72 is inputted to the first comparing and computing unit 85 to be used as
Current value PV1.Also, the desired value SP1 applied from first adder 87 is inputted to the first comparing and computing unit 85.In the first ratio
Compared with operational part 85, progress PID control is so that current value PV1 moves closer to desired value SP1, to the application of second adder 88 PID
Control output valve.In addition, however it is not limited to PID control or such as PI controls in the first comparing and computing unit 85.
The main steam temperature T2 from main steam temperature sensor 70, which is inputted, to the second comparing and computing unit 86 is used as present situation
Value PV2.Also, the main steam target that is determined is inputted in such as 550 DEG C~560 DEG C of scope to the second comparing and computing unit 86
Temperature is used as desired value SP2.In the second comparing and computing unit 86, PID control is carried out so that current value PV2 moves closer to target
Value SP2, PID control output valve is applied to first adder 87.In addition, however it is not limited to the PID controls in the second comparing and computing unit 86
System or such as PI controls.
Also, input the intermediate steam temperature T1 as the output valve from the first control function R1 to first adder 87
Anticipation temperature.Therefore, in first adder 87, main steam temperature T2 current value PV2 is compared relative to from second
Value corresponding to the main steam target temperature SP2 of operational part 86 deviation and the main steam applied by the first control function R1
The anticipation temperature of intermediate steam temperature T1 corresponding to target temperature is added, using the additive value as the first comparing and computing unit 85
Desired value SP1.
In addition to applying the PID control output valve from the first comparing and computing unit 85 to second adder 88, also to
Two adders 88 apply the go-ahead signal from the second control function R2.As these additive values from second adder 88
Output is applied separately and divided to the 3rd control function R3 and the 4th control function R4, opening degree command value as control output valve
The first steam flow adjustment valve 80 and second steam flow adjustment valve 81 is not applied to.
According to above-mentioned present embodiment, following action effect is realized.
Obtain determining the intermediate steam temperature T1 and main steam temperature T2's between No. 1 superheater 59 and No. 2 superheaters 61
First control function R1 of relation, controlled according to the measurement result of the first control function R1 and intermediate steam temperature sensor 72
The first steam flow adjustment valve 80 and second steam flow adjustment valve 81 is made, so that primary steam temperature T2 is desired value.Thus,
With only using as the main steam temperature T2 of steam stream most downstream come enter trip temperature adjust compared with, can not produce control delay and
Main steam temperature is set to turn into desired value.
Also, it is not to obtain the main steam temperature T2 in No. 2 exits of superheater 61, but obtains No. 1 superheater 59 and 2
Intermediate steam temperature T1 between secondary superheater 61 controls temperature, in steam stream upstream side limit temperature, therefore can avoid
The temperature of superheater 59,61 becomes too high situation.Thereby, it is possible to control the metal temperature of superheater 59,61 in setting
Below, it can be ensured that the viability of superheater 59,61.
In addition, for stove 31, No. 2 superheaters 61 are set in the rear side of No. 1 superheater 59, thus, with No. 1 superheater
59 compare, and No. 2 superheaters 61 is not readily susceptible to the radiation from stove.Accordingly, for than No. 1 time superheater 59 of steam stream on the lower
No. 2 superheaters 61 that trip side and metal temperature easily rise by steam, reduce the influence of radiation, thus enable that 2 overheats
The metal temperature of device 61 is to allow below temperature.
On the metal temperature of such superheater 59,61, illustrated using Fig. 5.No. 1 superheater is represented in the figure
The metal temperature of No. 59 and 2 superheaters 61.In the figure, transverse axis represents the flowing side of the steam flowed in superheater 59,61
Upward position, the longitudinal axis represent heat-transfer pipe 59a, 61a of superheater 59,61 metal temperature and flowed in superheater 59,61
Steam temperature.As shown in the drawing, it is No. 1 superheater 59 to make from first passage I to the 6th passage VI, is made from the 7th passage
VII to the tenth passage X is No. 2 superheaters 61.Also, the line of the upside in chart represents metal temperature, the line of downside represents to steam
Stripping temperature.
It was found from the figure, the metal temperature in first passage I is dramatically reduced after rising in upstream side, then further
Rise.The temperature drastically is produced for the reason for following to be reduced：Heat-transfer pipe 59a is reverse U shape shape (reference picture 2), in fire
The position of the side of stove 31 is radiated in the higher tendency of temperature, is not allowed in the position turned back along the direction away from stove 31
It is vulnerable to radiation, therefore in temperature than relatively low tendency.Identical is being also illustrated that from second channel II to the 6th passage VI
Tendency.Because No. 1 superheater 59 is configured at the position of the side of stove 31 relative to No. 2 superheaters 61.Therefore, logical from the 7th
In road VII to the tenth passage X, due to being not readily susceptible to the influence of radiation, therefore would not observe that in same passage drastically
Temperature reduces, and metal temperature represents the value close to vapor (steam) temperature.
On the other hand, in No. 1 superheater 59, due in steam stream upstream side, therefore compared with metal temperature, steam
Temperature is substantially low temperature.
It was found from the figure, vapor (steam) temperature reduces between fourth lane IV and Five-channel V.Because by delaying hot device
76 (reference pictures 3) reduce vapor (steam) temperature.Thus, no matter whether the metal temperature in the downstream of fourth lane is in the highest temperature
Degree, Five-channel V metal temperature is all low temperature compared with fourth lane IV metal temperature.So, by making to delay hot device 76
Between fourth lane IV and Five-channel V it is such by the half-way for radiating No. 1 superheater 59 influenceed and
Vapor (steam) temperature is reduced by delaying hot device 76, so as to control as the permission temperature not over the material for forming heat-transfer pipe 59a
Degree.
Also, in No. 2 superheaters 61, due to being not readily susceptible to the influence of radiation, therefore metal temperature will not be as 1 mistake
The fourth lane of hot device 59 is substantially increased like that.Therefore, the heat-transfer pipe 61a as No. 2 superheaters 61, can use and 1 mistake
The heat-transfer pipe 59a identical metal materials of hot device 59, due to that need not use advanced material therefore the increase of cost will not be caused.
Also, in addition to the control of the intermediate steam temperature T1 obtained by based on intermediate steam temperature sensor 72, also
Main steam temperature T2 according to measured by main steam temperature sensor 70, carried out using the second comparing and computing unit 86 (reference picture 4)
Control, so that primary steam temperature turns into desired value.It is accurate thereby, it is possible to which further main steam temperature T2 is micro-adjusted
Ground is controlled.
Also, as shown in figure 3, being not that bypass path 78 is provided with fixed orifice and turns into fixed aperture, but set
The first steam flow adjustment valve 80 is equipped with, valve opening can be adjusted.Such as cope with because of caused by the deterioration year in year out of stove
The increase of superheat steam temperature caused by the change of amount of heat absorption.That is, even if the second steam flow adjustment valve 81 is opened for 100%
Degree, also it can carry out the control of vapor (steam) temperature by increasing the aperture of the first steam flow adjustment valve 80.Thereby, it is possible to will steam
The metal temperature of the superheater 59,61 in vapour return 59f downstream is securely maintained lower than permissible value.
Also, it is the 10% of the defined aperture bigger than 0% by making the minimum aperture of the first steam flow adjustment valve 80,
It can prevent all steam that the steam taking-up portion 59e guiding from No. 1 superheater 59 comes from being flowed into slow hot device 76.Thus, energy
The generation of the condensed water because caused by reducing the temperature for delaying the steam in hot device 76 is enough prevented, and avoids condensed water from flowing into second
The generation of the unfavorable condition of steam flow adjustment valve 81.Further, it is possible to the operating that avoids following worry and can be stablized：
The larger pressure loss is produced in hot device 76 is delayed when substantial amounts of steam is flowed into slow hot device 76, steam taking-up portion 59e's is upper
The steam pressure of No. 1 superheater 59 for swimming side excessively rises, and then the steam pressure of steamdrum 43 excessively rises, and steam is from setting
The safety valve being placed in steamdrum 43 sprays.
In addition, in the above-described embodiment, be illustrated using reheat boiler peculiar to vessel as boiler 7 for one,
But the invention is not restricted to this or the marine boiler without reheater, it is not limited to stationary boiler peculiar to vessel.
Claims (9)
1. a kind of boiler, it is characterised in that have：
Burner, the burner are burnt in stove；
Evaporator, the evaporator produce steam by burning gases caused by the burner；
Superheater, the superheater is configured at the stove side relative to the evaporator, and makes steam caused by the evaporator
Overheat and produce superheated steam；
Vapor (steam) temperature adjustment unit, the overheat is returned to making the steam from the taking-up of the steam taking-up portion of the half-way of the superheater
During the steam return of device, the vapor (steam) temperature adjustment unit is adjusted to vapor (steam) temperature；
Control unit, the control unit control the vapor (steam) temperature adjustment unit；And
First temperature sensor, steam stream downstream of first temperature sensor to the steam return of the superheater
And the first vapor (steam) temperature of the half-way of the superheater measures,
The control unit has superheater outlet temperature relation information, and the superheater outlet temperature relation information is determined as institute
The superheater outlet temperature of the vapor (steam) temperature of the outlet of superheater and the relation of first vapor (steam) temperature are stated, according to the superheater
The measurement result of outlet temperature relation information and first temperature sensor controls the vapor (steam) temperature adjustment unit, so that
The superheater outlet temperature turns into desired value.
2. boiler according to claim 1, it is characterised in that
The boiler has the second temperature sensor measured to the superheater outlet temperature,
The control unit controls the vapor (steam) temperature adjustment unit according to the measurement result of the second temperature sensor, so that institute
Stating superheater outlet temperature turns into desired value.
3. boiler according to claim 1 or 2, it is characterised in that
The superheater has：No. 1 superheater, No. 1 superheater are arranged at steam stream upstream side；And No. 2 superheaters, this 2
Secondary superheater is arranged at the steam stream downstream of No. 1 superheater, after being arranged at No. 1 superheater relative to the stove
Side,
First vapor (steam) temperature measured by first temperature sensor is No. 1 superheater and No. 2 superheaters
Between vapor (steam) temperature.
4. the boiler described in any one in claims 1 to 3, it is characterised in that
The vapor (steam) temperature adjustment unit has：
Delay hot device, the temperature for delaying the steam that hot device carrys out guiding reduces；And
Delay hot device flow adjustment unit, this delays hot device and the stream for delaying the steam that hot device flows to this is adjusted with flow adjustment unit
Amount.
5. boiler according to claim 4, it is characterised in that
The vapor (steam) temperature adjustment unit has：Steam lead-in path, the steam lead-in path take out steam from the steam
Portion is directed to the slow hot device；Steam return path, the steam return path make steam return to the steaming from the slow hot device
Vapour return；And delaying hot device bypass path, this delays hot device bypass path in a manner of getting around the slow hot device by the steam
Lead-in path connects with the steam return path,
The slow hot device flow adjustment unit has：First flow adjusts valve, and first flow adjustment valve is arranged at described slow
Hot device bypass path；And second flow adjustment valve, second flow adjustment valve are arranged at the steam return path and described
Steam return path and the upstream side of the merging part for delaying hot device bypass path.
6. boiler according to claim 5, it is characterised in that
The minimum aperture of the first flow adjustment valve is the defined aperture bigger than 0.
7. a kind of marine vapor turbine propulsion system, it is characterised in that have：
Steamturbine, steamturbine driving produce the propeller of thrust in water；And
The boiler described in any one in claim 1 to 6, the boiler supply steam to the steamturbine.
A kind of 8. ship, it is characterised in that
The ship has the marine vapor turbine propulsion system described in claim 7.
9. a kind of boiler controlling method, it is characterised in that have：
Burning gases produce process, produce burning gases；
Steam produces process, and steam is produced by caused burning gases；
Superheated steam produces process, makes caused steam superheating and produces superheated steam in the superheater；
Superheated steam delays thermal technology sequence, and steam is taken out from the half-way of the superheater, and steam is made the steaming have passed through
The superheater is returned to after the slow hot device that the temperature of vapour reduces；
Delay hot device and adjust process with flow, the steam flowed to the slow hot device is adjusted by delaying hot device with flow adjustment unit
Flow；
First vapor (steam) temperature measures process, delays to have passed through the superheated steam after thermal technology sequence and the midway position of the superheater
The first vapor (steam) temperature put measures；And
Superheater outlet temperature adjusts process, and work is measured according to superheater outlet temperature relation information and first vapor (steam) temperature
The measurement result of sequence come control it is described delay hot device flow adjustment unit so that the superheater outlet temperature turns into desired value,
Wherein, the superheater outlet temperature relation information determines that the superheater of the vapor (steam) temperature of the outlet as the superheater goes out
The relation of mouth temperature and first vapor (steam) temperature.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015032868A JP6091020B2 (en) | 2015-02-23 | 2015-02-23 | Boiler, marine steam turbine propulsion system equipped with the same, ship equipped with the same, and boiler control method |
| JP2015-032868 | 2015-02-23 | ||
| PCT/JP2016/054167 WO2016136506A1 (en) | 2015-02-23 | 2016-02-12 | Boiler, marine steam turbine propulsion system equipped with same, ship equipped with same, and boiler control method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107614974A true CN107614974A (en) | 2018-01-19 |
| CN107614974B CN107614974B (en) | 2020-01-21 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680007926.0A Active CN107614974B (en) | 2015-02-23 | 2016-02-12 | Boiler, marine steam turbine propulsion system having the boiler, marine vessel having the propulsion system, and boiler control method |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6091020B2 (en) |
| KR (1) | KR101982955B1 (en) |
| CN (1) | CN107614974B (en) |
| WO (1) | WO2016136506A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110207100A (en) * | 2019-05-31 | 2019-09-06 | 四川陆亨能源科技有限公司 | A kind of novel convection-type desuperheater |
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|---|---|---|---|---|
| JPH0694210A (en) * | 1992-09-16 | 1994-04-05 | Babcock Hitachi Kk | Vapor temperature controller for boiler |
| JPH08121704A (en) * | 1994-10-20 | 1996-05-17 | Babcock Hitachi Kk | Steam temperature control apparatus for boiler |
| JPH1182920A (en) * | 1997-09-05 | 1999-03-26 | Mitsubishi Heavy Ind Ltd | Super-heated steam temperature control device in boiler |
| JP2006046670A (en) * | 2004-07-30 | 2006-02-16 | Daikin Applied Systems Co Ltd | Superheated steam cooking experimental device |
| JP2012167859A (en) * | 2011-02-14 | 2012-09-06 | Mitsubishi Heavy Ind Ltd | Marine boiler |
| JP5592305B2 (en) * | 2011-04-15 | 2014-09-17 | 株式会社神戸製鋼所 | Power generator |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS538844B2 (en) * | 1972-01-07 | 1978-04-01 | ||
| JPS5125602A (en) * | 1974-08-19 | 1976-03-02 | Mitsubishi Heavy Ind Ltd | Hakuyoboira oyobi sonojokiondochosetsuhoho |
| JPH0245313U (en) * | 1988-09-13 | 1990-03-28 | ||
| JPH0587308A (en) * | 1991-09-25 | 1993-04-06 | Mitsubishi Heavy Ind Ltd | Reducing device for superheated steam temperature |
| JP2006125760A (en) | 2004-10-29 | 2006-05-18 | Babcock Hitachi Kk | Exhaust heat recovery boiler and its control system |
| US8733104B2 (en) * | 2009-03-23 | 2014-05-27 | General Electric Company | Single loop attemperation control |
-
2015
- 2015-02-23 JP JP2015032868A patent/JP6091020B2/en active Active
-
2016
- 2016-02-12 WO PCT/JP2016/054167 patent/WO2016136506A1/en active Application Filing
- 2016-02-12 CN CN201680007926.0A patent/CN107614974B/en active Active
- 2016-02-12 KR KR1020177022677A patent/KR101982955B1/en active IP Right Grant
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0694210A (en) * | 1992-09-16 | 1994-04-05 | Babcock Hitachi Kk | Vapor temperature controller for boiler |
| JPH08121704A (en) * | 1994-10-20 | 1996-05-17 | Babcock Hitachi Kk | Steam temperature control apparatus for boiler |
| JPH1182920A (en) * | 1997-09-05 | 1999-03-26 | Mitsubishi Heavy Ind Ltd | Super-heated steam temperature control device in boiler |
| JP2006046670A (en) * | 2004-07-30 | 2006-02-16 | Daikin Applied Systems Co Ltd | Superheated steam cooking experimental device |
| JP2012167859A (en) * | 2011-02-14 | 2012-09-06 | Mitsubishi Heavy Ind Ltd | Marine boiler |
| JP5592305B2 (en) * | 2011-04-15 | 2014-09-17 | 株式会社神戸製鋼所 | Power generator |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110207100A (en) * | 2019-05-31 | 2019-09-06 | 四川陆亨能源科技有限公司 | A kind of novel convection-type desuperheater |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20170105065A (en) | 2017-09-18 |
| KR101982955B1 (en) | 2019-05-27 |
| JP6091020B2 (en) | 2017-03-08 |
| CN107614974B (en) | 2020-01-21 |
| JP2016156516A (en) | 2016-09-01 |
| WO2016136506A1 (en) | 2016-09-01 |
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